Calculating machine



G. C. CHASE CALCULATING MACHINE March 14, 1939.

8 Sheets-Sheet 1 Filed Nov, 27, 1935 INVENTOR GQObgZ. 0 Chase Y LfiwrronQn March 14, 1939.

G. c. CHASE CALCULATING MACHINE Filed Nov. 27, 1955 8 Sheets-Sheet 2 INVENTOR Ge C. Chase ATTORNEY March 14, 1939. G. c. CHASE CALCULATING MACHINE 8 Sheets-Sheet 3 INVENTOR G q e C Ch age MATTQRNEY Filed Nov. 2'7, 1935 March 14, 1939. c, CHASE CALCULATING MACHINE 8 Sheets-Sheet 4 Filed Nov. 27, 1935 cm m m w v w \V .wk L MW INVENTOR Gearge c. Ch M ATTORNEY March 14, 1939. G. c. CHASE CALCULATING MACHINE s ShetsSheet 5 Filed Nov. 27, 1935 a M m 1 March 14, 1939.

G. C CHASE CALCULATING MACHINE Filed Nov. 27, 1935 8 Sheets-Sheet 6 INVENTOR.

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March 14, 1939. c, CHASE 2,150,578

CALCULAT ING MACHINE Filed Nov. 27, 1935 8 Sheets-Sheet 7 WW Qw 'IIIIIIIIIIIIIIII k/myl wmmm March 14, 1939. 'G H SE 2,150,578

CALCULATING MACHINE Filed Nov. 27, 1935 8 Sheets-Sheet 8 IN VENTOR.

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Patented Mar. 14, 1939 UNITED STATES CALCULATING MACHINE George 0. Chase, South Orange, N. 3., assignor to Monroe Calculating Machine Company, Orange, N. J., a. corporation of Delaware Application November 27, 1935, Serial No. 51,810

19 Claims.

The invention relates to calculating machines and more particularly to an improved form of digit entering mechanism.

The invention consists in the novel construction and combination of parts, as set forth in the appended claims.

In the accompanying drawings illustrating the invention,

Fig. 1 is a right side elevation of a calculating machine embodying the invention; with the casing removed.

Fig. 2 is a vertical section, taken through the keyboard.

Fig. 3 is a partially diagrammatic view of a set of selector slides and associated parts Fig. 4 is a detail view of the bottom portion of the clear key.

Fig. 5 is a transverse section of an actuator gear unit.

"I Fig, 6 is a section taken on line 6-6 of Figure 5.

Fig. 7 is an enlarged vertical section of the selector and registering mechanism.

Fig. 8 is a view illustrating a modified form of actuator gearing, shown in transverse section.

Fig. 9 is a section, taken on line 99 of Figure 8.

Fig. 10 is a plan view of the selector pinion adjusting means, with parts shown in section.

:0 Fig. 11 is a developed cross sectional view through a numeral wheel and its associated driving pinion and tens transfer elements.

Fig. 12 is a side elevation of the numeral wheel and associated parts, with parts shown in section.

Fig. 13 is a plan view of certain numeral wheel locating mechanisms.

Fig. 14 is a front elevation showing two rows of keys and the related selector slides, parts being shown in section.

Fig. 15 is a detail face view of a portion of the variable speed drive gearing. -The invention is shown as applied to a reversible cycle calculating machine which, in order 5 to simplify the disclosure, is operated by means of a reversible crank handle 3. The mechanisms involved are however primarily designed for high speed operation, and it will be obvious that a machine of this kind could be equipped with a motor drive such, for instance, as that disclosed in U. S. Patent No. 1,566,650, issued to George C. Chase on December 22, 1925.

In the drawings, a reversible crank handle 3 (Fig. 1) has driving connection with a train of gears 4, designed todrive a shaft 5 in one-to-one ratio with said handle. Shaft 5, through gearing 1 (Fig. 2), and shaft 8, operates certain constantly driven portions of the machine, as will later appear, and also provides an intermittent drive for the differential actuators of the machine, by means of a mechanism disclosed in U. S. Patent No. 1,858,763, issued to George C. Chase on May 17, 1932.

It is desired to hold the actuators inactive during the first quarter cycle of crank handle movement; to give them a harmonically accelerated and diminished movement during the second and third quarters of the cycle, and to hold them at rest during the final quarter. For this purpose, an elliptic gear 33, fixed upon shaft 5, meshes with an elliptic gear 34, (Figs. 1 and 5) loosely mounted on stud 39 and having planetary gear connection with the actuator drive gear 35 also loosely mounted on stud 39. This connection comprises a pair of connected planet pinions 36 and 31, eccentrically mounted on the elliptic gear 34, and a sun gear 38 loosely mounted on the stud 39 supporting said elliptic gear. Drive gear 35 meshes with pinion 31, while sun gear 38 meshes with pinion 36 and also with the teeth of segment 40, having anti-friction roller engagement with a pair of cams 4|, fast upon shaft 5.

Cams 4| are designed to give the desired movement to the drive gear 35, the elliptic gears 33 and 34 serving to cooperate in the driving of gear 35 and, by approximating the desired drive ratios, to lighten the work of the cams 4|.

Gear 35 drives pinions 42 and 43, fast upon the hubs of a pair of pinion wire gears 44 and 45 (Fig. 2) extending across the machine. An idler gear 46 is interposed between gear 35 and pinion 43, to reverse the direction of rotation of the pinion wire gear 45 relative to the gear 44.

A locator cam I53 is fast with one of the gears 4, and is engaged by the anti-friction roller of a locator arm I55, exerting pressure upon said cam by means of a spring I56.

Digit entering mechanism For each column of digit selecting keys I8 there is provided three trains of gears 41, 48 and 49 (Figs. 3 and 10) movable in planetary manner about a shaft 50 to engage one or the other of the pinion wires 44 or 45. Gear train 41, as will be shown later, when engaged with either of the pinion wires 44 or 45, effects movement of the differential actuator gearing to register a single unit on the numeral wheels |3 of an accumulating register, during a complete rotation of crank handle I. The train 48 similarly registers three units on the numeral wheels, and trains ll registers a single unit. This registering movement of the wheel may either be like or unlike the sign of the operation being performed (dependent upon the directim of rotation of crank handle. 3) according to whether pinion wire 44 or pinion wire 46 is engaged by a gear of the train. The gear trains 41, I8 and 40 may be engaged singly or in groups with the pinion wires, the effective values of the trains being aggregated or the difference obtained by the differential actuator gearing with which they mesh. The numerals at the top of Figure 3 represent diagrammatically the digit selecting keys, and the lower numerals, read in vertical columns, give the components which are involved in the registration of each of the key values. For instance 6 is registered as +10, -l, -3; 2 will be registered as +3, 1, etc. This provides a system of short cutting similar to that described in the co-pending Hilder application, Serial No. 3,088, filed January 23, 1935,'modii'ied by the use of combined plus and minus registrations, to reduce the number of different setting movements to be effected.

In each column, the gears of the trains 41, ll and II are set to the desired positions by means of four selector slides II, 52, I3 and 54, each provided with cam lugs I5, lying under the stems of the keys ll (l 'igazand 14). The rearward ends of slides II and I! are pivotally connected to plates ll adapted for arcuate movement about the shaft lil by means of rod and guide slot supports II. The rear end of slide it is provided with a rack, engaging the lower teeth of a pinion II, mounted on the right hand plate I1, and the rearward end of slide 84 is provided with a rack engaging the upper teeth of the pinion ll of the right hand plate 61 in the next higher order column, so that each right hand plate 51 is differentially controlled to the setting of keys in its own column and in the lower order column. The plates I! each carry the two pinions of the train ll, II or ll, so that forward or rearward movement of a selector slide will rock the gear of such train into mesh with pinion wire 44 or 45; In this movement, the inner gear of the train will advance around its cooperating actuator gear 58, ll or II, giving a rotary movement to me outer gear of the train which will compensate for its movement relative to the pinion wire, bringing the teeth of the gear into mesh with the teeth of the pinion wire by movement substantially radial to such wire. The rollers II of the selector :lides engage between the teeth of a guide comb When the selector slides stand in their intermediate, sero position, the actuator gears 58, II and II are locked by means of detents N (Fig. 2) having cam slots engaged by pins of the plates 51. Movement of a plate 61 from neutral position in either direction, will operate to cam its detent out of engagement between the teeth of the actuator gear. During the operative portion of each cycle of the machine, the plates 81 are locked in one of their three adjusted positions by means of a ball 04, having an arm ll engaging a pin of the locator arm I" (Fig. 1), whereby the ball will be rocked into engagement between the teeth of racks 00 formed in the plates 51.

It will be noted that the selector slides are movable in either direction from intermediate, zero position, these slides being shown as urged forwardly by springs I1, and slides Ill, 52 being normally held in intermediate position by the gamers stems of the depressed aerokeys. The keys of each column, including the zero key, are engaged'by a locking bail 8, cooperating with the customary shoulders on the key stems inFig. 14 whereby a do pressed key is held locked in its depressed position, against the tension of its return spring, until another key in the same column is depressed, whereupon the original key is released in the manner common to "flexlble keyboards. Therefore, upon depression of any keyfl to 9 in a column, the related zero key will be released, and the appropriate selector slide will either be allowed to move into its forward position, or will be cammed rearwardly by engagement of the key stem with a cam lug it of the slide. It is therefore necessary to set the slides ii, 52, I3 and 54, against the tension of the springs 81, in clearing the keyboard of the machine, this being done by the depression of the zero keys, as in U. 8. Patent No. 1,750,565, issued to E. F. Britten, Jr. on March 11, 1930.

For this purpose, the stems of the zero keys are provided with lugs 88 (Fig. 2) engageable by a bail 68, extending across the front of the machine and having an arm Ill (Figs. 1 and 4) underlying the stem of a. clear key ll. Automatic clearing or non-repeat mechanism is provided by means of a lever 12 settable into or out of cooperating relation with a cam tooth 14, carried by crank handle I in well known manner. Lever 12 overlies the arm 10 of bail 68 and, when set-to active position, a

depresses all of the zero keys, during the final portion of the cycle of crank handle I.

The differential actuators consist of a series of orbital gear units, related each to a column of keys, and being preferably of the planetary gear type. The gears 59, 60 and BI constitute each a leg of the differential (Figs. 5 and 6). The hubs of each of the gears 59 and ii are provided with sun gear teeth, engaging planet pinions ll, carried in annular supports 16. There are two sets of the pinions 15, one set transmitting movement from the sun gear teeth of gear 58 or from a set of internal gear teeth of the gear BI to the annull 16 supporting the pinions, the other set of planetary pinions (Fig. 6) transmitting movement from the sun gear teeth of gear 6| to the internal gear teeth of an output gear 80.

Plates 18 (Figs. 7 and 13), engaging comb 1' and shouldered shaft Ti, serve to locate the differential actuator gear units in proper position on the shaft 50 and to support the rods 58.

Assuming the gears 88, and 6| to be operated one after the other, the following actions would occur in the orbital gear train:

Gear 59 being rotated forwardly, the sun gear teeth thereof will rotate forwardly and, the internal gear teeth of gear 80 being held stationary, the annuli It will be moved forwardly, by the action of the planet pinions 15. Gear 6 I, with its sun gear teeth, being also held against movement,

the output gear 80 will be carried forwardly,

through the action of the planet pinions upon its internal teeth. The ratio of the gears involved in this operation is such that gear 80 receives a four tooth movement during each cycle of the ma-' chine, this corresponding to a single unit Ynovement of the numeral wheel, as will be seen.

Gear 80 being now driven forwardly, while the sun gear teeth of gear 59 are held stationary, the annulus 16 will be moved forwardly and, sun gear teeth of gear 6i being also held stationary, the output gear 80 will be moved forwardly, in this instance for a twelve tooth advance or registration of three on the numeral wheels.

Finally, ear 8i being advanced, and the annulus it being held stationary, because oi. the locking of the sun and ring gears related to the gears 59 and the output gear 86 will he moved four teeth, or one registering unit, in a reverse direction.

An inspection of F gure 3 will show how each of the digits, from 1 to 8, is set up in the actuator gearing, the method of setting up a plural figure item being illustrated in the following examples:

It may be noted that in setting the 5 the +10, together with the +3 in the tens column provides for a total plus movement of the output gear 88 of sixteen teeth, but that the -1 in the tens column provides for a counteracting movement of gear 59, so that the output gear of this tens column will be advanced twelve teeth, for a registering of 3. A second example serves to illustrate a different condition:

The register The digit entering mechanism forming the subject matter of the present invention may advantageously be combined with a direct wheel to wheel tens transfer mechanism.

Such a tens transfer mechanism is disclosed in the U. 8. Patent to Chase No. 1,964,314, issued June 26, 1934. This comprises a direct gearing connection between the numeral wheels of the register, the gearing being of the entocyclic type, distinguishing from epicyclic gearing in that a floating gear is carried in an eccentric orbit within the circumference of an internal gear. Registrations according to the setting of pinions 41, 48, 49 (Figs 7 and 10) are transmitted to the numeral wheel i3 through gear 80, pinions I0 and II (Fig. 11) and the eccentrically mounted floating gear I4. The orbital gearing is so designed that for each unit of value selected by the pinions, gear 80 will transmit a four tooth movement or a third of a rotation to the pinion II secured to the eccentric hub of floating gear I4. This floating gear has external and. internal teeth, the latter engaging the teeth of a pinion 26 and the former engaging an internal gear I5, secured to the numeral wheel I3. The floating gear has three more internal teeth than are provided on pinion 26, and three less external teeth than internal gear it, so that a 120 degree eccentric movement or the floating gear it within the gear will impart a one tooth movement to the numeral wheel in the well lmown manner. Geared to each mumeral wheel it is a plate it upon which is mounted a transfer roller I8 movable through the teeth of a star Wheel 23, fast with the pinion 26. This will impart .9, direct gear movement to the float= ing gear It, to register the tens transfer. Plate I8 forms a locking plate acting upon a detent 2i, and thereby upon the star wheel 23, to prevent overthrow of the tens transfer mechanism. Lost motion is taken out of the gear train connection between the numeral wheels, and the tenstransfor is completed at the end of each cycle, by means of a series of successively acting alignor cams 28, operating upon the detents 21 through an intermediate member 30. These alignors are secured upon the numeral wheel supporting shaft II, which is driven through gearing 8|, pinion wire 82, and gearing 83 (Figs. 7, 11 and 12), from a through shaft 8, connected by gearing I (Fig. 2) with the constantly driven shaft 5, previously referred to.

The numeral wheels I3 (together with the usual revolution counting wheels 84) and the related tens transfer mechanism are mounted in a transversely shiftable carriage 2, and in order to hold the numeral wheel gearing in alignment during a shifting movement of said carriage a comb 85 (Figs. 7 and 13) is provided, through the teeth of which comb the gears I0 pass as they move out of engagement with the gears 80. As the gears iii are moved laterally beyond the base of the machine, they are locked by the action of spring detents 86. The detents 86 related to the gears Ill which are in mesh with the gears 80 of the machine are held out of contact with such gears III by means of rollers 81 of the detents engaging a track 88 formed by the outer face of the comb 85, which is supported in the base of the machine,

Alternative dz'fie ential actuator A modified form of differential actuator gearing is shown in Figs. 8 and 9, in which the digits 1 to 9, or 1 to 11 (in the case of calculations in twelfths), are registered normally, instead of by the shortcut method hereinbefore described.

Two pinionwire gears, I80, I8I, are employed, gear I80 being rotated once during each rotation of the crank handle of the machine and gear I8I being driven two-to-one, in the same direction as gear I88, by means of the gearing I82.

This drive arrangement is one of several optional constructions, since it will be obvious that equally driven shafts, with gears of different di- -ameter, or the oppositely driven shafts hereinbefore described, might be used. The only essential is that the two drive elements shall transmit rotary movements differing, in thecase of one element and the other, either in degree or in direction.

For each differential actuator (related to a column of keys) there is provided three trains of gears I83, I84, I85, adjustable in planetary manner about a shaft I86 to engage one or the other of the pinion wires I88, I8I. The gears of trains I83 and I85 are of simple intermediate character, transmitting movement tooth for tooth from the pinion wire to the actuator gears I81 and I88 respectively. In the form illustrated, these" gears each have 12 teeth. Gear train I84,

however. includes a compound gear I89, whereby the movement transmitted from pinion wire III to the actuator gear I81 is stepped up onehalf. Each of the trains I88, I84, I80 is mounted on a plate I90, similar to the plates 81, herein before described.

Each differential actuator consists of a train of orbital gearing of the entocyclic type, the gears I81 and I89 constituting each a leg of the differential. Gear I81 is provided with an eccentric hub III, upon which is mounted a floating pinion I92, meshing with the internal teeth of an output gear I93. There is a difference of nine teeth between pinion I92 and these internal teeth. Gear III has a pin and recess coupling I94 with the floating pinion, so designed that any movement of said gear will be transmitted to the pinion but, upon movement of gear I81 allowing the pinion to be carried around within the gear I93. by rotation of the hub I9I, independently of any movement of gear I88.

The outer gear of train I83 being meshed with the pinion wire I80 and the gear I88 held stationary by means similar to those previously described, a full rotation of I80 will effect a halfrotation of the eccentric hub NH. The pins I94 will prevent rotation of pinion I92 upon its axis during this movement, so that the difference in the number of teeth between pinion I92 and output gear I93 will cause the latter to rotate about shaft I89. According to the gear ratios shown, output gear I93 will be advanced a distance corresponding to three of its external teeth for each rotation of pinion wire I90, when gear train I83 is engaged, suitable compound gearing I95 serving to step up this movement so that the numeral wheel of Fig. '7 will be advanced a single digit space. Alternatively, compound gearing I95 may be omitted, and the twelve tooth pinion wire I80 driven one and a third revolutions during each cycle of the machine. with pinion wire I 8I, numeral wheel I3 will be advanced two'steps, while engagement of train I84 with pinion wire I8I will advance the numeral wheel three steps during each cycle of operation.

Gear train I88 being adjusted to mesh with pinion wire I80, and gear I81 held stationary, a full rotation of I00 will effect a half-rotation of floating pinion I92 upon its axis, the gear ratios shown being such that this will result in a four step advance of numeral wheel I3. Similarly, engagement of train I88 with pinion wire I8I will effect an eight step advance of the numeral wheel.

Thus registrations of l, 2 and 3 are provided for by leg I81 of the differential, and registrations of 4 and 8 by leg I88, different combinations of the two legs giving the figures 5, 6, 7, 9, l0 and 11.

It is to be observed that gear trains I83 and I84 may not be simultaneously driven, and in the construction shown. meshing of train I84 with pinion wire I80 is not useful, since the registration would be 1 also that the combinations, useful in registering in twelfths (as in British currency calculations, for example) would be omitted in decimal calculations.

I claim:

1. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element, orbital gear compound differential actuators each including gear elements forming each a leg of the diflerential normally disengaged from and indi- Train I83 being engaged vidually engageable with one or alternatively with the other drive element and having direct gear connection with the accumulating register, and devices selectively settable to effect simultaneous engagement of a plurality of gear elements related to a single actuator.

2. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element, orbital gear compound differential actuators each including three gear elements forming each a leg of the differential normally disengaged from and individually engageable with one or alternatively with the other drive element, and an output gear having direct gear connection with the accumulating register and adapted to receive movement by different combinations of the three gear elements and two drive elements corresponding to any selected one of nine different digits.

3. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element, orbital gear differential actuators each including two gear elements forming each a leg of the differential normally disengaged from and individually engageable with one or alternatively with the other drive element, and an output gear having direct gear connection with the accumulating register and adapted to receive movement by different combinations of the two gear elements and two drive elements corresponding to any selected one of eight different digits.

4. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, orbital gear differential actuators each including gear elements forming each a leg of the differential and having direct gear connection with the accumulating register, trains of shiftable gears engaging said orbital gear elements and individually settable from disengaged position into engagement with the drive element and including two gear trains of different transmission ratio engaging a single orbital gear element, and devices selectively scttable to effect simultaneous engagement of a plurality of gear trains related to a single actuator.

5. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element, orbital gear differential actuators each including gear elements forming each a leg of the differential and having direct gear connection with the accumulatirm register, trains of shiftable gears engaging said orbital gear elements and individually settable from disengaged position into engagement with one or alternatively with the other drive element and including two gear trains of different transmission ratio, engaging a single orbital gear element, and devices selectively settable to effect simultaneous engagement of a plurality of gear trains related to a single actuator,

6. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element, a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element, orbital gear differential actuators each including two gear elements forming cach'a leg of the differential, three trains of shiftable gears of two diflerent transmission ratios engaging said orbital gear elements and individually settable from disengaged position into engagement with one or alternatively with the other drive element. and an output gear having direct gear connection with the accumulating register and adapted to receive movement by different combinations of the two gear elements, three gear trains and two drive elements corresponding to any selected one of eleven different values.

7. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, diiferential actuators each including elements having direct gear connections with the accumulating register, individually engageable with said drive gearing and adapted to register the sum of the values of the engaged elements,

and means settable to control said engagement, including bars individual to the orbital gear elementsand operable to engage the related elements selectively with the drive gearing of one or the other drive shaft, and keys each settable to control a selected group of bars.

8. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, orbital gear differential actuators each including elements having direct gear connection with the accumulating register and individually engageable with said drive gearing, and means settable to control said engagement, including bars individual to the orbital gear elements and operable to engage the related elements selectively with the drive gearing of one or the other drive shaft, and keys each settable to control a selected group of bars.

9. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, orbital gear differential actuators each including elements individually engageable with said drive gearing and a common output gear having direct gear connection with the accumulating register, and means settable to control said engagement, including bars individual to the orbital gear elements and each operable to engage the related element selectively with the drive gearing of one or the other drive shaft, said bars being settable in groups, to efiect movement of the output gear in accordance with the sum of or alternatively with the difference between the driven movements of the orbital gear elements.

10. In a calculating machine, an accumulating register, digit entering mechanism including planetary gear compound differential actuators having direct gear connection with the accumulating register and each comprising two sun gears, two sets of planet pinions, two annular gears, and a floating annulus carrying the planet pinions of both sets, and operating means for said actuators.

11. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, selective ratio differential actuator gearing including ratio determining elements having direct gear connection with the accumulating register and individuallly engageable with said drive gearing, and devices settable to control the engagement of said ratio determining elements with the drive gearing of one or the other drive shaft, to register certain selected digit values normally and other selected digit values complementally.

12. In a calculating machine, an accumulating register, digit entering mechanism comprising reversible, oppositely rotatable drive shafts, drive gearing thereon, selective ratio diflerential actuator gearing having direct gear connection with the accumulating register and including ratio determining elements individually engageable with said drive gearing, devices settable tocontrol the engagement of said ratio determining elements with the drive gearing of one or the other drive shafts, to register certain selected digit values normally and other selected digit values complementally, and means for'reversing the direction of rotation of said drive shafts.

13. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, differential actuators each including elements having direct gear connection with the accumulating register, individually engageable with said drive gearing and adapted to register the sum of the values of the engaged elements, and means settable to control said engagement, including devices settable to control the engagement of said elements with the drive gearing, to register certain selected digit values complementally, including a device settable to engage a related element with the drive gearing of one of said shafts, and a lower order device settable to engage said element with the drive gearing of the other shaft.

14. In a calculating machine, an accumulating register, digit entering mechanism comprising oppositely rotatable drive shafts, drive gearing thereon, selective ratio differential actuator gearing having direct gear connection with the accumulating register and including ordinal series of ratio determining elements individually engageable with said drive gearing, and ordinal series of devices settable to control the engagement of said ratio determining elements with the drive gearing, to register certain selected digit values complementally, including a device settable to engage a related determining element with the drive gearing of one of said shafts, and a lower order device settable to engage said element with the drive gearing oi' the other shaft.

15. In a calculating machine, an accumulating register, digit entering mechanism comprising a drive element. a second drive element adapted to transmit a different rotary movement from that transmitted by the first named element,- selective ratio differential actuator gearing having direct gear connection with the accumulating register, including ratio determining elements individually engageable with said drive elements and adapted to register the sum of the values of the engaged elements, and means for engaging said elements singly'or in combination with the drive elements of one or the other drive shaft.

16. In a calculating machine, an accumulating register, digit entering mechanism comprising a pinion wire drive gear, a second parallel pinion wire drive gear adapted to transmit a different rotary movement from that transmitted by the first named gear, selective ratio differential actuator gearing having direct gear connection with the accumulating register and including ratio determining elements individually engageable with said drive gearing, a series of digit keys, and bars settable singularly or in combination by said keys forwardly or reversely from an ineffective median position to effect engagement of said ratio determining elements with the drive gearing of one or the other drive shaft.

17. In a calculating machine, an accumulating parallel drive shafts, drive gearing thereon, selective ratio diflerential actuator gearing having direct gear connection with the accumulating register and including ratio determining elements individually engageable with said drive gearing, and settable devices including spring urged bars, latches holding said bars in ineflective partially advanced position, and selective means for releasing or advancing said bars to effect engagement oi said ratio determining elements with the drive gearing of one or the other drive shaft.

18. In a calculating machine, an accumulating register, digit entering mechanism comprising two parallel drive shafts, drive gearing thereon, selective ratio differential actuator gearing having direct gear connection with the accumulating register and including ordinal series of ratio determining elements individually engageable with said drive gearing, ordinal series of settable devices including spring urged bars, latches holding said bars in ineffective partially advanced position, and selectively settable keys for releasing or advancing said bars to effect engagement of said ratio determining elements with the 2,180,578 register, digit entering mechanism comprising two drive gearing of one or the other drive shaft. and power operated means comprising key release elements and bar engaging elements, for re-engaging all 01' the released or advanced bars with their latches.

19. In a calculating machine, an accumulating register, digit entering mechanism comprising two parallel drive shafts, drive gearing thereon, selective ratio diflerential actuator gearing having direct gear connection with the accumulating register and including ratio determining elements individually engageabie with said drive gearing, and settable devices including spring urged bars adapted in retracted position to engage said ratio determining elements with the drive gearing of one shaft and in fully advanced position to engage said elements with the drive gearing oi the other shaft, a zero key adapted to cam said bars to ineffective partially advanced position, a series of digit keys certain of which are adapted to fully advance certain of said bars, and a latch common to said digit keys and zero key, adapted upon depression of any key to hold down said key and to release a previously depressed key.

GEORGE C. CHASE. 

